EP3577404B1 - Condenseur - Google Patents

Condenseur Download PDF

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Publication number
EP3577404B1
EP3577404B1 EP18702870.9A EP18702870A EP3577404B1 EP 3577404 B1 EP3577404 B1 EP 3577404B1 EP 18702870 A EP18702870 A EP 18702870A EP 3577404 B1 EP3577404 B1 EP 3577404B1
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EP
European Patent Office
Prior art keywords
heat transfer
transfer tubes
refrigerant
shell
condenser
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP18702870.9A
Other languages
German (de)
English (en)
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EP3577404A1 (fr
Inventor
Louis A. MOREAUX
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
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Daikin Industries Ltd
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Publication date
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Publication of EP3577404A1 publication Critical patent/EP3577404A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1638—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one
    • F28D7/1646—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one with particular pattern of flow of the heat exchange medium flowing outside the conduit assemblies, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • F28F9/0131—Auxiliary supports for elements for tubes or tube-assemblies formed by plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0224—Header boxes formed by sealing end plates into covers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/046—Condensers with refrigerant heat exchange tubes positioned inside or around a vessel containing water or pcm to cool the refrigerant gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • F28D2021/0063—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/007—Condensers

Definitions

  • This invention generally relates to a condenser adapted to be used in a vapor compression system. More specifically, this invention relates to a condenser including a vapor passage.
  • Vapor compression refrigeration has been the most commonly used method for air-conditioning of large buildings or the like.
  • Conventional vapor compression refrigeration systems are typically provided with a compressor, a condenser, an expansion valve, and an evaporator.
  • the compressor compresses refrigerant and sends the compressed refrigerant to the condenser.
  • the condenser is a heat exchanger that allows compressed vapor refrigerant to condense into liquid.
  • a heating/cooling medium such as water typically flows through the condenser and absorbs heat from the refrigerant to allow the compressed vapor refrigerant to condense.
  • the liquid refrigerant exiting the condenser flows to the expansion valve.
  • the expansion valve expands the refrigerant to cool the refrigerant.
  • the refrigerant from the expansion valve flows to the evaporator.
  • This refrigerant is often two-phase.
  • the evaporator is a heat exchanger that allows the refrigerant to evaporate from liquid to vapor while absorbing heat from the heating/cooling medium passing through the evaporator.
  • the refrigerant then returns to the compressor.
  • the heating/cooling medium can be used to heat/cool the building.
  • JP 2015-064157 A relating to a condenser for a compression refrigerator, in EP0962734A2 , relating to a heat exchanger and in US 1641975A , relating to a heat exchanger with self-draining tube surface.
  • one object of the present invention is to provide a condenser with a large number of tubes and excellent heat transfer performance.
  • another object of the present invention is to provide a condenser, in which vapor can flow around those tubes so that the vapor pressure drop between the compressor discharge and the condenser tubes can be reduced.
  • the tube layout can contribute to the pressure drop between the compressor discharge and the condenser tubes.
  • another object of the present invention is to provide a tube layout of the heat transfer tubes in the condenser, which creates a flow passage to allow the vapor to flow down and reach the bottom tubes more easily by reducing pressure drop.
  • yet another object of the present invention is to provide a condenser, in which vapor can flow around those tubes so that the vapor pressure drop between the compressor discharge and the condenser tubes can be reduced when LPR refrigerant is used.
  • One or more of the above objects can basically be attained by providing condenser adapted to be used in a vapor compression system according to claim 1.
  • the condenser includes a shell and a tube bundle.
  • the shell has a refrigerant inlet that at least refrigerant with gas refrigerant flows therethrough and a refrigerant outlet that at least refrigerant with liquid refrigerant flows therethrough, with a longitudinal center axis of the shell extending generally parallel to a horizontal plane.
  • the tube bundle includes a plurality of heat transfer tubes disposed inside of the shell so that the refrigerant discharged from the refrigerant inlet is supplied onto the tube bundle.
  • the heat transfer tubes extend generally parallel to the longitudinal center axis of the shell.
  • the plurality of heat transfer tubes in the tube bundle are arranged to form a first vapor passage extending generally vertically along a first passage lengthwise direction through at least some of the heat transfer tubes of the tube bundle.
  • the first vapor passage has a first minimum width measured perpendicularly relative to the first passage lengthwise direction and the longitudinal axis.
  • the first minimum width is larger than a tube diameter of the heat transfer tubes of the tube bundle, and the first minimum width is smaller than four times the tube diameter.
  • the vapor compression system according to the first embodiment is a chiller that may be used in a heating, ventilation and air conditioning (HVAC) system for air-conditioning of large buildings and the like.
  • HVAC heating, ventilation and air conditioning
  • the vapor compression system of the first embodiment is configured and arranged to remove heat from liquid to be cooled (e.g., water, ethylene glycol, brine, etc.) via a vapor-compression refrigeration cycle, and to add heat to liquid to be heated (e.g., water, ethylene glycol, calcium chloride brine, etc.) via a vapor-compression refrigeration cycle.
  • Water is shown in the illustrated embodiment. However, it will be apparent to those skilled in the art from this disclosure that other liquids can be used. Heating and cooling of the liquid is shown in the illustrated embodiment.
  • the vapor compression system includes the following main components: an evaporator 1, a compressor 2, the condenser 3, an expansion device 4, and a control unit 5.
  • the control unit 5 is operatively coupled to a drive mechanism of the compressor 2 and the expansion device 4 to control operation of the vapor compression system.
  • the control unit may also be connected to various other components such as sensors and/or optional components of the system not shown.
  • the evaporator 1 is a heat exchanger that removes heat from the liquid to be cooled (in this example, water) passing through the evaporator 1 to lower the temperature of the water as a circulating refrigerant evaporates in the evaporator 1.
  • the refrigerant entering the evaporator I is typically in a two-phase gas/liquid state.
  • the refrigerant at least includes liquid refrigerant.
  • the liquid refrigerant evaporates as the vapor refrigerant in the evaporator 1 absorbs heat from the cooling medium such as water.
  • the evaporator 1 uses water as a heating/cooling medium as mentioned above.
  • the evaporator 1 can be any one of numerous conventional evaporators, such as a falling film evaporator, flooded evaporator, hybrid evaporator, etc.
  • the water exiting the evaporator is cooled. This cooled water can then be used to cool the building or the like.
  • the refrigerant Upon exiting the evaporator 1, the refrigerant will be low pressure low temperature vapor refrigerant.
  • the low pressure, low temperature vapor refrigerant is discharged from the evaporator 1 and enters the compressor 2 by suction.
  • the compressor 2 the vapor refrigerant is compressed to the higher pressure, higher temperature vapor.
  • the compressor 2 may be any type of conventional compressor, for example, centrifugal compressor, scroll compressor, reciprocating compressor, screw compressor, etc.
  • the high temperature, high pressure vapor refrigerant enters the condenser 3, which is another heat exchanger, which removes heat from the vapor refrigerant causing it to condense from a gas state to a liquid state.
  • the condenser 3 in the illustrated embodiment is liquid cooled using a liquid such as water.
  • the heat of the compressed vapor refrigerant raises the temperature of cooling water passing through the condenser 3.
  • the hot water from the condenser is routed to a cooling tower to reject the heat to the atmosphere.
  • the heated water (cooling water that cools the refrigerant) can be used in a building as a hot water supply or to heat the building.
  • the condensed liquid refrigerant then enters the expansion device 4 where the refrigerant undergoes an abrupt reduction in pressure.
  • the expansion device 4 may be as simple as an orifice plate or as complicated as an electronic modulating thermal expansion valve. Whether the expansion device 4 is connected to the control unit will depend on whether a controllable expansion device 4 is utilized.
  • the abrupt pressure reduction usually results in partial expansion of the liquid refrigerant, and thus, the refrigerant entering the evaporator 1 is usually in a two-phase gas/liquid state.
  • refrigerants used in the vapor compression system are hydrofluorocarbon (HFC) based refrigerants, for example, R410A, R407C, and R134a, hydrofluoro olefin (HFO), unsaturated HFC based refrigerant, for example, R1234ze, and R1234yf, and natural refrigerants, for example, R717 and R718.
  • HFC hydrofluorocarbon
  • HFO hydrofluoro olefin
  • unsaturated HFC based refrigerant for example, R1234ze, and R1234yf
  • natural refrigerants for example, R717 and R718.
  • R1234ze, and R1234yf are mid density refrigerants with densities similar to R134a.
  • R450A and R513A are mid pressure refrigerants that are also possible refrigerants.
  • a so-called Low Pressure Refrigerant (LPR) R1233zd is also a suitable type
  • Low Pressure Refrigerant (LPR) R1233zd is sometimes referred to as Low Density Refrigerant (LDR) because R1233zd has a lower vapor density than the other refrigerants mentioned above.
  • R1233zd has a density lower than R134a, R1234ze, and R1234yf, which are so-called mid density refrigerants.
  • the density being discussed here is vapor density not liquid density because R1233zd has a slightly higher liquid density than R134A. While the embodiment(s) disclosed herein are useful with any type of refrigerant, the embodiment(s) disclosed herein are particularly useful when used with LPR such as R1233zd. R1233zd is not flammable. R134a is also not flammable.
  • R1233zd has a global warming potential GWP ⁇ 10.
  • R134a has a GWP of approximately 1300.
  • Refrigerants R1234ze, and R1234yf are slightly flammable even though their GWP is less than 10 like Rt 233zd. Therefore, R1233zd is a desirable refrigerant due to these characteristics, non-flammable and low GWP.
  • the refrigerant preferably includes R1233zd. More preferably, in the illustrated embodiment, the refrigerant preferably is Rt 233zd. As mentioned above, R1233zd is a desirable refrigerant due to its low GWP and not being flammable. However, in a condenser in which a maximum number of heat transfer tubes are included (to try to maximize efficiency) as shown in FIG.
  • compressor 2 the evaporator 1 and the expansion device 4
  • the compressor 2, the evaporator 1 and the expansion device 4 are conventional components that are well known in the art. Since the compressor 2, the evaporator 1 and the expansion device 4 are well known in the art, these structures will not be discussed or illustrated in detail herein. Rather, it will be apparent to those skilled in the art from this disclosure that any suitable compressor, evaporator and expansion device can be used with the condenser of the illustrated embodiment. Therefore, the following descriptions will focus on the condenser 3 in accordance with the present invention.
  • the vapor compression system may include a plurality of evaporators 1, compressors 2 and/or condensers 3 without departing the form the scope of the present invention.
  • the condenser 3 basically includes a shell 10, a refrigerant distributor 20, and a heat transferring unit 30.
  • the heat transferring unit 30 is a tube bundle.
  • the heat transferring unit 30 will also be referred to as the tube bundle 30 herein.
  • the tube bundle 30 carries a liquid cooling/heating medium such as water therethrough.
  • Refrigerant enters the shell 10 and is supplied to the refrigerant distributor 20.
  • the refrigerant distributor 20 is configured to relatively evenly distribute the refrigerant onto the tube bundle 30, as explained in more detail below.
  • the refrigerant entering the shell 10 of the condenser 3 is a compressed gas (vapor) refrigerant that is typically at high pressure and high temperature.
  • the vapor refrigerant will exit the distributor 20 and flow into the interior of the shell 10 onto the tube bundle 30.
  • the vapor refrigerant will gradually cool and condense as it flows down over the tube bundle 30.
  • the medium (water) in the tube bundle 30 absorbs heat from the vapor refrigerant to cause this condensation and cooling to occur.
  • the condensed liquid refrigerant will then exit the bottom of the condenser, as explained in more detail below.
  • the shell 10 has a generally cylindrical shape with a longitudinal center axis C ( FIG. 4 ) extending generally in the horizontal direction.
  • the shell 10 extends generally parallel to a horizontal plane P and the center axis C is generally parallel to the horizontal plane P.
  • the shell 10 includes a connection head member 13, a cylindrical body 14, and a return head member 15.
  • the cylindrical body 14 is hermetically attached between the connection head member 13 and the return head member 15.
  • the connection head member 13 and the return head member 15 are hermetically fixedly coupled to longitudinal ends of the cylindrical body 14 of the shell 10.
  • the connection head member 13 includes an attachment plate 13a, a dome part 13b attached to the attachment plate 13a and a divider plate 13c extending between the attachment plate 13a and the dome part 13b to define an inlet chamber 13d and an outlet chamber 13e.
  • the attachment plate 13a is normally a tube sheet that is normally welded to the cylindrical body 14.
  • the dome part 13b is normally attached to the tube sheet (attachment plate) 13a using bolts and a gasket (not shown) disposed therebetween.
  • the divider plate 13c is normally welded to the dome part 13b.
  • the inlet chamber 13d and the outlet chamber 13e are divided from each other by the divider plate 13c.
  • the return head member 15 also includes an attachment plate 15a and a dome member 15b attached to the attachment plate 15a to define a return chamber 15c.
  • the attachment plate 15a is normally a tube sheet that is normally welded to the cylindrical body 14.
  • the dome part 15b is normally attached to the tube sheet (attachment plate) 15a using bolts and a gasket (not shown) disposed therebetween.
  • the return head member 15 does not include a divider.
  • the attachment plates 13a and 15a are fixedly coupled to longitudinal ends of the cylindrical body 14 of the shell 10.
  • the inlet chamber 13d and the outlet chamber 13e are partitioned by the divider plate (baffle) 13c to separate flow of the cooling medium.
  • connection head member 13 is fluidly connected to both an inlet pipe 17 through which water enters and a water outlet pipe 18 through which the water is discharged from the shell 10. More specifically, the inlet chamber 13d is fluidly connected to the inlet pipe 17, and the outlet chamber 13e is fluidly connected to the outlet pipe 18, with the divider plate 13c dividing the flows.
  • the attachment plates 13a and 15a include a plurality of holes with heat transfer tubes 34a and 34b mounted therein.
  • the tubes 34a form an upper group of heat transfer tubes while the tubes 34b form a lower group of heat transfer tubes.
  • the heat transfer tubes 34a and 34b can be positioned in the holes and then roller expanded to secure the tubes 34a and 34b within the holes and form a seal therebetween.
  • a lower group of the heat transfer tubes 34b receive water from the inlet chamber 13d and carry the water through the cylindrical body 14 to the return chamber 15c. The water in the return chamber 15c then flows into an upper group of the heat transfer tubes 34a back through the cylindrical body 14 and into the outlet chamber 13e.
  • the condenser 3 is a so-called "two pass" condenser 3.
  • the flow path of the water is sealed from an interior space of the cylindrical body 14 between the attachment plates 13a and 15a.
  • This interior space contains refrigerant sealed from the water flow path.
  • the tube bundle 30 includes an upper group of the heat transfer tubes 34a and a lower group of the heat transfer tubes 34b disposed below the upper group of the heat transfer tubes 34a.
  • the upper group of the heat transfer tubes 34a is disposed at or above a vertical middle plane (e.g., the plane P in FIG. 4 ) of the shell 10, and the lower group of the heat transfer tubes 34b is disposed at or below the vertical middle plane (e.g., the plane P in FIG. 4 ) of the shell 10. More specifically, in the illustrated embodiment, the upper group of the heat transfer tubes 34a is disposed at and above a vertical middle plane (e.g., the plane P in FIG. 4 ) of the shell 10, and the lower group of the heat transfer tubes 34b is disposed below the vertical middle plane (e.g., the plane P in FIG. 4 ) of the shell 10.
  • a vertical middle plane e.g., the plane P in FIG. 4
  • the lower group of the heat transfer tubes 34b is disposed below the vertical middle plane (e.g., the plane P in FIG. 4 ) of the shell 10.
  • the upper and lower groups are separated by a gap and have approximately (or generally) the same number of heat transfer tubes 34a and 34b in each group (e.g. within a few percent) so that water can flow in generally the same manner (e.g., velocity/volume) through the upper and lower groups of the heat transfer tubes 34a and 34b.
  • the tube counts of the heat transfer tubes 34a and 34b can be selected to be close enough to each other so that adverse water flow issues do not occur.
  • the shell 10 further includes a refrigerant inlet 11a connected to a refrigerant inlet pipe 11b and a refrigerant outlet 12a connected to a refrigerant outlet pipe 12b.
  • the refrigerant inlet pipe 11b is fluidly connected to the compressor 2 to introduce compressed vapor gas refrigerant supplied from the compressor 2 into the top of the shell 10. From the refrigerant inlet 11a the refrigerant flows into the refrigerant distributor 20, which distributes the refrigerant over the tube bundle 30. The refrigerant condenses due to heat exchange with the tube bundle 30. Once condensed within the shell 10, liquid refrigerant exits the shell 10 through the refrigerant outlet 12a and flows into the refrigerant outlet pipe 12b.
  • the expansion device 4 is fluidly coupled to the refrigerant outlet pipe 12b to receive the liquid refrigerant.
  • the refrigerant that enters the refrigerant inlet 1 1a includes at least gas refrigerant.
  • the refrigerant that flows through the refrigerant outlet 12a includes at least liquid refrigerant.
  • the shell 10 has a refrigerant inlet 11a that at least refrigerant with gas refrigerant flows therethrough and a refrigerant outlet 12a that at least refrigerant with liquid refrigerant flows therethrough, with a longitudinal center axis C of the shell extending generally parallel to the horizontal plane P.
  • the refrigerant distributor 20 is fluidly connected to the refrigerant inlet 11a and is disposed within the shell 10.
  • the refrigerant distributor 20 is arranged and configured with a dish configuration to receive the refrigerant entering the shell 10 through the refrigerant inlet 1 1a.
  • the refrigerant distributor 20 extends longitudinally within the shell 10 generally parallel to the longitudinal center axis C of the shell 10.
  • the refrigerant distributor 20 includes a base part 22, a first side part 24a, a second side part 24b, and a pair of end parts 26.
  • the base part 22, first side part 24a, the second side part 24b, and the pair of end parts 26 are rigidly connected together.
  • each of the base part 22, first side part 24a, the second side part 24b, and the pair of end parts 26 is constructed of thin rigid plate material such as steel sheet material.
  • the base part 22, first side part 24a, the second side part 24b, and the pair of end parts 26 can be constructed as separate parts fixed to each other or can be integrally formed as a one-piece unitary member.
  • a plurality of holes are formed in the base part 22, first side part 24a, and the second side part 24b.
  • the end parts 26 are free of holes.
  • the base part 22 has circular holes formed therein except at end areas as best understood from FIG. 5 .
  • the side parts 24a and 24b have circular holes formed therein, except at end areas.
  • longitudinal slots are formed at the end areas of the side parts 24a and 24b, however, unlike the base part 22, longitudinal slots are formed. The longitudinal ends beyond the end areas have holes formed therein like the middle areas.
  • the distributor 20 is welded to the upper portion of the shell 10.
  • the distributor 20 may be fixed to support plates (discussed below) of the tube bundle 30.
  • the end parts 26 may be omitted if not needed and/or desired.
  • the end parts 26 of the distributor 20 are present and have upper ends with curves matching an internal curvature of the cylindrical shape of the cylindrical body 14 shell 10.
  • the distributor 20 has a length almost as long as an internal length of the shell 10. Specifically, in the illustrated embodiment, the distributor has a length at least about 90% as long as an internal length of the shell 10, e.g., about 95%. Thus, refrigerant is distributed from the distributor 20 along almost an entire length of the tube bundle 30.
  • the tube bundle 30 is disposed below the refrigerant distributor 20 so that the refrigerant discharged from the refrigerant distributor 20 is supplied onto the tube bundle 30.
  • the tube bundle 30 includes a plurality of support plates 32, a plurality of heat transfer tubes 34a and 34b (mentioned briefly above) that extend generally parallel to the longitudinal center axis C of the shell 10 through the support plates 32, and a plurality of plate support members 36, as best shown in FIGS. 4-6 .
  • a guide plate 40 is disposed below the tube bundle 30. The guide plate 40 collects condensed liquid (refrigerant) and directs that liquid to the condenser outlet 12a at the bottom of the shell 10.
  • the support plates 32 are shaped to partially match an interior shape of the shell 10 to be fitted therein.
  • the guide plate 40 is disposed under the support plates 32.
  • the heat transfer tubes 34a and 34b extend through holes formed in the support plates 32 so as to be supported by the support plates 32 within the shell 10.
  • the plate support members 36 are attached to the support plates 32 to support and maintain the support plates 32 in the spaced arrangement relative to each other, as shown in FIGS. 4-5 . Once the support plates 32 and plate support members 36 are attached together as a unit (e.g., by welding), the unit can be inserted into the cylindrical body 14 and can be attached thereto, as explained below in more detail.
  • each support plate 32 is preferably formed of a rigid sheet material such as sheet metal.
  • each support plate 32 has a flat plate shape and includes curved sides shaped to match an interior curvature of the shell, and upper and lower notches extending generally toward each other. Due to the mating curved shapes of the support plates 32 and the cylindrical body 14 the support plates 32 are prevented from moving vertically, laterally, etc. (e.g., in any direction transverse to the longitudinal center axis C) relative to the cylindrical body 14.
  • the guide plate 40 is disposed under the support plates 32. The guide plate 40 can be fixed to the cylindrical body 14 or may merely rest inside the cylindrical body 14.
  • the guide plate 40 may be fixed to the support plates 32 or the support plates may merely rest on the guide plate 40.
  • the guide plate 40 is fixed (e.g., welded) to the cylindrical body 14 before assembly of the support plates 32 and the plate support members 36 is inserted and attached to the cylindrical body 14.
  • the assembly is inserted into the cylindrical body 14 on top of the guide plate 40, and then the end ones of the support plates 32 are welded to the cylindrical body 14 of the shell 10.
  • the upper notches of the support plates 32 form a recess shaped to make space for the distributor 20.
  • the distributor 20 is welded to the cylindrical body 14 such that the distributor 20 is disposed within the upper notches.
  • the distributor 20 may be fixed to the support plates 32 or the distributor 20 may rest on the support plates 32.
  • the support plates 32 are not fixed to the distributor 20 so that the distributor 20 can be attached to the cylindrical body 14 before or after the tube bundle 30 as a unit.
  • the lower notches of the support plates 32 together form a fluid flow channel.
  • the guide plate 40 is mounted within the shell 10 to extend parallel to the longitudinal center axis C and parallel to the plane P under the support plates 32 as mentioned above.
  • the refrigerant condenses and changes state into liquid refrigerant.
  • This condensed liquid refrigerant flows along the guide plate 40 toward the ends of the condenser 3.
  • the guide plate 40 is shorter than the cylindrical body 14. Thus, the liquid refrigerant then flows downward and then along the bottom of the cylindrical body 14 to the refrigerant outlet 12a.
  • the support plates 32 have a plurality of holes formed therein. Almost all of the holes receive heat transfer tubes 34a and 34b therethrough. However, a few of the holes receive the plate support members 36. In the illustrated embodiment, six of the holes receive these members 36. Specifically, on each side of the tube bundle, in the illustrated embodiment, three of the plate support members 36 extend through holes in the support plates 32 and are fixed to the support plates 32 to maintain the support plates 32 in the spaced arrangement illustrated herein.
  • the guide plate 40 can further provide vertical support to the bottom of the tube bundle 30, as best understood from FIGS. 5-6 .
  • the plate support members 36 are constructed as elongated, rigid, rod-shaped members. One suitable material is steel.
  • the heat transfer tubes 34a and 34b extend through the remaining holes of the support plates 32 so as to be supported by the support plates 32 in the pattern illustrated herein.
  • the heat transfer tubes 34a and 34b may be fixed to the support plates 32 or merely supported by the support plates 32. In the illustrated embodiment, the heat transfer tubes 34a and 34b only rest on and are not fixed to the support plates 32.
  • the plate support members 36 have diameters smaller than diameters of the heat transfer tubes 34a and 34b. In the illustrated embodiment, the plate support members 36, and the heat transfer tubes 34a and 34b have circular cross-sectional shapes.
  • the diameters of the plate support members 36 are smaller than the heat transfer tubes 34a and 34b, even though the plate support members 36 are mounted to the outer sides of the support plates 32 vapor flow passages can be created, which are not significantly hindered by the presence of the plate support members 36. This will be explained in more detail below.
  • the heat transfer tubes 34a and 34b are made of materials having high thermal conductivity, such as metal.
  • the heat transfer tubes 34a and 34b are preferably provided with interior and exterior grooves to further promote heat exchange between the refrigerant and the water flowing inside the heat transfer tubes 34a and 34b.
  • Such heat transfer tubes including the interior and exterior grooves are well known in the art.
  • GEWA-C tubes by Wieland Copper Products, LLC may be used as the heat transfer tubes 34a and 34b of this embodiment.
  • the heat transfer tubes 34a and 34b are supported by the plurality of vertically extending support plates 32, which are supported within the shell 10.
  • the tube bundle 30 is arranged to form a two-pass system, in which the heat transfer tubes 34a and 34b are divided into a supply line group of tubes 34b disposed in a lower portion of the tube bundle 30, and a return line group of tubes 34a disposed in an upper portion of the tube bundle 30.
  • inlet ends of the heat transfer tubes 34b in the supply line group are fluidly connected to the inlet pipe 17 via the inlet chamber 13d of the connection head member 13 so that water entering the condenser 3 is distributed into the heat transfer tubes 34b in the supply line group.
  • Outlet ends of the heat transfer tubes 34b in the supply line group and inlet ends of the heat transfer tubes 34a of the return line group are fluidly communicated with the return chamber 15c of the return head member 15. Therefore, the water flowing inside the heat transfer tubes 34b in the supply line group is discharged into the return chamber 15c, and redistributed into the heat transfer tubes 34a in the return line group. Outlet ends of the heat transfer tubes 34a in the return line group are fluidly communicated with the outlet pipe 18 via the outlet chamber 13e of the connection head member 13. Thus, the water flowing inside the heat transfer tubes 34a in the return line group exits the condenser 3 through the outlet pipe 18.
  • the supply line group may include an additional group of plates and tubes under the guide plate 40 (i.e., a sub-cooler below the guide plate 40), such as is illustrated in FIG. 12 .
  • communicating holes should be formed at the bottom of the plates under the guide plate 40 or cutouts should be formed so that liquid refrigerant can flow along the bottom of the condenser to the refrigerant outlet 12a. Refrigerant should already be liquid once the refrigerant has descended to the guide plate 40.
  • additional heat transfer tubes under the guide plate 40 can be used in order to further lower the temperature of the liquid under the guide plate 40 (i.e., to sub-cool) before exiting the condenser.
  • an additional outlet from the condenser 3 can be provided if a supply of condensed liquid refrigerant is needed for some other purpose (e.g., for motor cooling or any other purpose). Such an additional outlet from the condenser is shown in FIG. 12 .
  • the plate support members 36 are attached to the support plates 32 (e.g., by welding) to form a tube bundle unit.
  • the guide plate 40 can be inserted in and fixed (e.g., welded) to the shell 10 before or after assembly of the support plates 32 and the plate support members 36.
  • the distributor 20 can be inserted in and fixed (e.g., welded) to the shell 10 before or after assembly of the support plates 32 and the plate support members 36.
  • the assembled tube bundle unit including the support plates 32 and the plate support members 36 is inserted into the cylindrical body 14, after attaching the distributor 20 and the guide plate 40 in the illustrated embodiment.
  • the end pieces of the support plates 32 are then fixed (e.g., welded) to the cylindrical body 14.
  • the tube sheets 13a and 15a are attached (e.g., by welding) to the cylindrical body 14.
  • the heat transfer tubes 34a and 34b are inserted through the holes in the tube sheets 13a and 15a and through the support plates 32.
  • the heat transfer tubes 34a and 34b can then be roller expanded into the tube sheets 13a and 15a to secure the heat transfer tubes 34a and 34b.
  • the tube bundle 30 includes the plurality of heat transfer tubes 34a and 34b disposed inside of the shell 10 so that the refrigerant discharged from the refrigerant inlet 11a is supplied onto the tube bundle 30, with the heat transfer tubes 34a and 34b extending generally parallel to the longitudinal center axis C of the shell.
  • the plurality of heat transfer tubes 34a in the tube bundle are arranged to form at least a first vapor passage V1 extending generally vertically along a first passage lengthwise direction D1 through at least some of the heat transfer tubes 34a of the tube bundle 30.
  • the plurality of heat transfer tubes 34a in the tube bundle are arranged to form a second vapor passage V2 extending generally vertically along a second passage lengthwise direction D2 through at least some of the heat transfer tubes 34a of the tube bundle 30.
  • a pair of vapor passages V1 and V2 are provided.
  • the vapor passages V1 and V2 are provided in order to reduce a pressure drop, which in turn limits reduction in cycle efficiency (cycle efficiency can be generally maintained).
  • the vapor passages V1 and V2 are provided through the upper group of heat transfer tubes 34a but not through the lower group of heat transfer tubes 34b.
  • the vapor passages V1 and V2 can also extend through the lower group of heat transfer tubes 34b (in addition to the upper group of heat transfer tubes 34a). In any case, the vapor passages V1 and V2 at least extend through the upper group of heat transfer tubes 34a as illustrated in this embodiment.
  • the vapor passages V1 and V2 are provided at least through the upper group of heat transfer tubes 34a where there is a higher concentration of vapor than in the lower group of the heat transfer tubes 34b.
  • the vapor passage V1 has a first minimum width W1 measured perpendicularly relative to the first passage lengthwise direction D1 and the longitudinal axis C.
  • the first minimum width W1 is larger than a tube diameter DO of the heat transfer tubes of the tube bundle 30, and the first minimum width W1 is smaller than four times the tube diameter DO.
  • minimum gaps between the heat transfer tubes 34b in the lower group and the shell 10 are smaller than tube diameter DO.
  • a vapor passage is intended to mean a gap or width W1 or W2 at least as large as the tube diameter DO and smaller than four times the tube diameter DO.
  • the first minimum width W1 is larger than twice the tube diameter DO and smaller than three times the tube diameter. In the illustrated embodiment, the first minimum width W1 is about 2.5 times the tube diameter DO. Gaps between the remaining tubes 34a in the upper group are larger than W1, e.g., ranging from between slightly less than three times the tube diameter DO to slightly less than four times the tube diameter DO (bottom row tube and 3 rd from the bottom row tube of the upper group). Likewise, in the illustrated embodiment, the second minimum width W2 is larger than twice the tube diameter DO.
  • the vapor passages V1 and V2 are mirror images of each other, and thus, it will be apparent to those skilled in the art from this disclosure that that descriptions/illustrations of one side also apply to the other side. Moreover, it will be apparent to those skilled in the art from this disclosure that this embodiment is merely one example, and that the upper part of the condenser 3 could be replaced with the upper part of the condenser of the second embodiment, discussed below, and vice versa.
  • the first vapor passage V1 is formed between the tube bundle 30 and a first longitudinal sidewall (e.g., a first lateral side of the cylindrical body 14) of the shell 10.
  • the second vapor passage V2 is formed between the tube bundle 30 and a second longitudinal sidewall (e.g., a second opposite lateral side of the cylindrical body 14) of the shell 10. This can best be seen in FIG. 7 .
  • the first and second lengthwise directions D1 and D2 are arc-shaped and extend along an interior of the cylindrical body 14.
  • the first and second vapor passages V1 and V2 are formed between the upper group of heat transfer tubes 34a and the cylindrical body 14 (opposing first and second longitudinal sidewalls) of the shell 10.
  • FIG. 11 illustrates a relationship of COP (Coefficient of Performance) versus Condenser pressure drop.
  • COP Coefficient of Performance
  • COP Coefficient of Performance
  • a condenser i.e., by theoretically maximizing heat transfer
  • larger pressure drops can occur when the number of heat transfer tubes is maximized, which can decrease COP.
  • no appreciable drop in COP is caused by removing the tubes to make the vapor passage(s) explained and illustrated herein, and in fact COP can be improved as shown in FIG. 11 ..
  • the configurations of the vapor passages V1 and V2 are identical mirror images of each other, it will be apparent to those skilled in the art from this disclosure that these vapor passages do not have to be identical.
  • the exact clearances can be optimized using Computational Fluid Dynamics (CFD) and will vary depending on the size of the system, size of the condenser, size of the heat transfer tubes, etc.
  • CFD Computational Fluid Dynamics
  • W1 about 30 mm
  • W2 about 30 mm.
  • the gap between the lower group is smaller than DO and thus, does not form a passage as define herein.
  • the gap between the smaller group can be larger than DO to further form passages (e.g., about 20 mm), as explained with reference to the second embodiment.
  • a condenser 203 in accordance with a second embodiment of the present invention is illustrated.
  • the condenser 203 is identical to the condenser 3 of the first embodiment, except the layout (pattern) of the heat transfer tubes 34a and 34b has been modified so that modified first and second vapor passages 2V1 and 2V2 are formed in accordance with this second embodiment.
  • the descriptions and illustrations of the first embodiment also apply to this second embodiment, except as explained herein.
  • the same reference numerals are used for parts of this second embodiment as identical or functionally identical parts of the first embodiment.
  • modified first and second vapor passages 2V1 and 2V2 are formed in accordance with this second embodiment, which extend along arc-shaped first and second passage lengthwise directions 2D1 and 2D2, respectively.
  • modified support plates 232 are provided with hole patterns matching the layout of FIG. 9 . Otherwise, the support plates 232 are identical to the support plates 32 of the first embodiment.
  • the first vapor passage 2V1 extends through the upper group of the heat transfer tubes 34a and the lower group of the heat transfer tubes 34b.
  • an upper first minimum width UW1 of the first vapor passage 2V1 passing through the upper group of the heat transfer tubes 34a is larger than a lower first minimum width LW1 of the first vapor passage 2V1 passing through the lower group of the heat transfer tubes 34b.
  • the second vapor passage 2V2 extends through the upper group of the heat transfer tubes 34a and the lower group of the heat transfer tubes 34b.
  • an upper second minimum width UW2 of the second vapor passage 2V2 passing through the upper group of the heat transfer tubes 34a is larger than a lower second minimum width LW2 of the second vapor passage 2V2 passing through the lower group of the heat transfer tubes 34b.
  • the first upper minimum width UW1 is larger than 1.5 times the tube diameter DO and smaller than three times the tube diameter DO. In the illustrated embodiment, the first upper minimum width UW1 is slightly smaller than two times the tube diameter DO. Gaps between the remaining tubes 34a in the upper group are larger than UW1, e.g., ranging from about two times the tube diameter DO to slightly less than three times the tube diameter DO (bottom row tube and 3 rd from the bottom row tube of the upper group). Likewise, in the illustrated embodiment, the second upper minimum width UW2 is larger than 1.5 times the tube diameter DO and smaller than three times the tube diameter DO. In the illustrated embodiment, the vapor passages 2V1 and 2V2 are mirror images of each other, and thus, it will be apparent to those skilled in the art from this disclosure that that descriptions/illustrations of one side also apply to the other side.
  • this embodiment is merely one example, and that the upper part of the condenser 203 could be replaced with the upper part of the condenser 3 of the first embodiment, discussed above, and vice versa.
  • the lower parts of the passages 2V1 and 2V2 are vertical mirror images of the upper parts, except an additional tube is added to the top row and the third from the top row on each side such that the gaps LW1 and LW2 are smaller than UW1 and UW2, respectively, and the maximum gap size is also smaller.
  • additional tubes e.g., 5 could be added on each side of the lower group such as are illustrated in FIGS.
  • the first and second passage lengthwise directions 2D1 and 2D2 are identical to the first and second passage lengthwise directions D1 and D2, respectively, except the first and second passage lengthwise directions 2D1 and 2D2 continue along the curvature of the cylindrical body 14 through the lower group of the heat transfer tubes.
  • the upper first minimum width UW1 can be slightly smaller than the first width W1 of the first embodiment as illustrated herein (e.g., 10%) or can be identical.
  • the lower first minimum width LW1 of the first vapor passage 2V1 passing through the lower group of the heat transfer tubes 34b can be for example 20 mm as mentioned above.
  • the upper second minimum width UW2 of the second vapor passage 2V2 passing through the upper group of the heat transfer tubes 34a can be slightly smaller than the second width W2 of the first embodiment as illustrated herein (e.g., 10%) or can be identical.
  • the lower second minimum width LW2 of the second vapor passage 2V2 passing through the lower group of the heat transfer tubes 34b can be for example 20 mm as mentioned above.
  • UW1 about 30 mm
  • UW2 about 30 mm
  • LW1 about 20 mm
  • LW2 about 20 mm.
  • both sides are mirror identical images of each other.
  • the following directional terms “upper”, “lower”, “above”, “downward”, “vertical”, “horizontal”, “below” and “transverse” as well as any other similar directional terms refer to those directions of a condenser when a longitudinal center axis thereof is oriented substantially horizontally as shown in FIGS. 4 and 5 . Accordingly, these terms, as utilized to describe the present invention should be interpreted relative to a condenser as used in the normal operating position. Finally, terms of degree such as “substantially”, “about” and “approximately” as used herein mean a reasonable amount of deviation of the modified term such that the end result is not significantly changed.

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Claims (15)

  1. Condenseur (3) adapté pour être utilisé dans un système de compression de vapeur, le condenseur comprenant :
    une enveloppe (10) ayant une entrée de réfrigérant (11a) à travers laquelle s'écoule au moins un réfrigérant avec un réfrigérant gazeux et une sortie de réfrigérant (12a) à travers laquelle s'écoule au moins un réfrigérant avec un réfrigérant liquide, un axe central longitudinal de l'enveloppe s'étendant généralement parallèlement à un plan horizontal ; et
    un faisceau de tubes (30) comportant une pluralité de tubes (34a, 34b) de transfert de chaleur disposés à l'intérieur de l'enveloppe de sorte que le réfrigérant évacué depuis l'entrée de réfrigérant soit acheminé sur le faisceau de tubes, les tubes de transfert de chaleur s'étendant de manière généralement parallèle à l'axe central longitudinal de l'enveloppe,
    la pluralité de tubes de transfert de chaleur dans le faisceau de tubes étant agencés pour former un premier passage de vapeur s'étendant de manière généralement verticale le long d'une première direction de longueur de passage à travers au moins certains des tubes de transfert de chaleur du faisceau de tubes, le premier passage de vapeur étant formé entre le faisceau de tubes et une paroi latérale longitudinale de l'enveloppe,
    caractérisé en ce que
    le premier passage de vapeur ayant une première largeur minimale mesurée perpendiculairement par rapport à la première direction de longueur de passage et à l'axe longitudinal, la première largeur minimale étant plus grande qu'un diamètre de tube des tubes de transfert de chaleur du faisceau de tubes, et la première largeur minimale étant plus petite que quatre fois le diamètre de tube.
  2. Condenseur selon la revendication 1, dans lequel
    la première largeur minimale est plus grande que deux fois le diamètre de tube.
  3. Condenseur selon l'une quelconque des revendications 1 à 2, dans lequel
    le faisceau de tubes comporte un groupe supérieur des tubes de transfert de chaleur et un groupe inférieur des tubes de transfert de chaleur disposé au-dessous du groupe supérieur des tubes de transfert de chaleur, et le premier passage de vapeur s'étend à travers au moins le groupe supérieur des tubes de transfert de chaleur.
  4. Condenseur selon la revendication 3, dans lequel
    le premier passage de vapeur s'étend à travers le groupe supérieur des tubes de transfert de chaleur et le groupe inférieur des tubes de transfert de chaleur.
  5. Condenseur selon la revendication 4, dans lequel
    la première largeur minimale du premier passage de vapeur traversant le groupe supérieur des tubes de transfert de chaleur est plus grande que la première largeur minimale du premier passage de vapeur traversant le groupe inférieur des tubes de transfert de chaleur.
  6. Condenseur selon l'une quelconque des revendications 3 à 5, dans lequel
    le groupe supérieur des tubes de transfert de chaleur est disposé au niveau ou au-dessus d'un plan médian vertical de l'enveloppe, et le groupe inférieur des tubes de transfert de chaleur est disposé au niveau ou au-dessous du plan médian vertical de l'enveloppe.
  7. Condenseur selon la revendication 1, dans lequel
    la pluralité de tubes de transfert de chaleur dans le faisceau de tubes sont en outre agencés pour former un deuxième passage de vapeur s'étendant de manière généralement verticale le long d'une deuxième direction de longueur de passage à travers au moins certains des tubes de transfert de chaleur du faisceau de tubes, et
    le deuxième passage de vapeur présente une deuxième largeur minimale mesurée perpendiculairement par rapport à la deuxième direction de longueur de passage et à l'axe longitudinal, la deuxième largeur minimale étant plus grande que le diamètre de tube des tubes de transfert de chaleur du faisceau de tubes, et la deuxième largeur minimale étant plus petite que quatre fois le diamètre de tube.
  8. Condenseur selon la revendication 7, dans lequel
    la première largeur minimale est plus grande que deux fois le diamètre de tube, et la deuxième largeur minimale est plus grande que deux fois le diamètre de tube.
  9. Condenseur selon la revendication 7 ou la revendication 8, dans lequel
    le premier passage de vapeur est formé entre le faisceau de tubes et une première paroi latérale longitudinale de l'enveloppe, et le deuxième passage de vapeur est formé entre le faisceau de tubes et une deuxième paroi latérale longitudinale de l'enveloppe opposée à la première paroi latérale longitudinale de l'enveloppe.
  10. Condenseur selon l'une quelconque des revendications 7 à 9, dans lequel
    le faisceau de tubes comporte un groupe supérieur des tubes de transfert de chaleur et un groupe inférieur des tubes de transfert de chaleur disposé au-dessous du groupe supérieur des tubes de transfert de chaleur, le premier passage de vapeur s'étend à travers au moins le groupe supérieur des tubes de transfert de chaleur, et le deuxième passage de vapeur s'étend à travers au moins le groupe supérieur des tubes de transfert de chaleur.
  11. Condenseur selon la revendication 10, dans lequel
    le premier passage de vapeur s'étend à travers le groupe supérieur des tubes de transfert de chaleur et le groupe inférieur des tubes de transfert de chaleur, et
    le deuxième passage de vapeur s'étend à travers le groupe supérieur des tubes de transfert de chaleur et le groupe inférieur des tubes de transfert de chaleur.
  12. Condenseur selon la revendication 11, dans lequel
    la première largeur minimale du premier passage de vapeur traversant le groupe supérieur des tubes de transfert de chaleur est plus grande que la première largeur minimale du premier passage de vapeur traversant le groupe inférieur des tubes de transfert de chaleur, et la deuxième largeur minimale du deuxième passage de vapeur traversant le groupe supérieur des tubes de transfert de chaleur est plus grande que la deuxième largeur minimale du deuxième passage de vapeur traversant le groupe inférieur des tubes de transfert de chaleur.
  13. Condenseur selon l'une quelconque des revendications 10 à 12, dans lequel
    le groupe supérieur des tubes de transfert de chaleur est disposé au niveau ou au-dessus d'un plan médian vertical de l'enveloppe, et le groupe inférieur des tubes de transfert de chaleur est disposé au niveau ou au-dessous du plan médian vertical de l'enveloppe.
  14. Condenseur selon l'une quelconque des revendications 1 à 13, dans lequel
    le réfrigérant est le R1233zd.
  15. Système de compression de vapeur comprenant :
    un évaporateur (1) ;
    un compresseur (2) ;
    le condenseur (3) selon l'une quelconque des revendications précédentes ;
    un détendeur (4) ; et
    une unité de commande (5).
EP18702870.9A 2017-02-03 2018-01-17 Condenseur Active EP3577404B1 (fr)

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US15/423,778 US10612823B2 (en) 2017-02-03 2017-02-03 Condenser
PCT/US2018/013946 WO2018144215A1 (fr) 2017-02-03 2018-01-17 Condenseur

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EP3577404B1 true EP3577404B1 (fr) 2023-05-03

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JP (1) JP6894520B2 (fr)
CN (1) CN110249196A (fr)
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Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112313464B (zh) * 2018-07-27 2024-02-02 开利公司 制冷剂容器部件和包括这样的制冷剂容器部件的制冷回路
CN109682245B (zh) * 2018-12-25 2020-07-28 四川大学 一种基于流体换热的温差发电装置
CN111750570A (zh) * 2019-03-28 2020-10-09 开利公司 蒸发器及其挡板结构
EP3832247B1 (fr) * 2019-12-03 2023-09-20 Carrier Corporation Évaporateur noyé
US11841031B2 (en) 2020-03-13 2023-12-12 Honeywell International Inc. Compressor sensor mount
US11635091B2 (en) 2020-03-13 2023-04-25 Honeywell International Inc. Compressor with integrated accumulator
CN115371296A (zh) 2021-05-21 2022-11-22 开利公司 用于冷凝器的水室结构、具有其的冷凝器及制冷系统
CN115615054B (zh) * 2022-09-27 2023-07-07 广东省安佳空调制冷有限公司 一种降幕式冷凝器

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1641975A (en) * 1926-04-08 1927-09-13 Griscom Russell Co Heat exchanger with self-draining tube surface
EP0962734A2 (fr) * 1998-06-02 1999-12-08 Electric Boat Corporation Echangeur de chaleur

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3167927A (en) * 1961-06-23 1965-02-02 Carrier Corp Promotion of dropwise condensation
US3861460A (en) * 1973-05-23 1975-01-21 Laval Turbine Condenser construction
US6269867B1 (en) * 1994-12-02 2001-08-07 Hitachi, Ltd Condenser and power plant
JP3735405B2 (ja) * 1995-12-15 2006-01-18 株式会社東芝 復水器
JP3572250B2 (ja) 2000-10-24 2004-09-29 三菱重工業株式会社 冷凍機用凝縮器
US6830099B2 (en) * 2002-12-13 2004-12-14 American Standard International Inc. Falling film evaporator having an improved two-phase distribution system
US6868695B1 (en) * 2004-04-13 2005-03-22 American Standard International Inc. Flow distributor and baffle system for a falling film evaporator
TWI292467B (en) * 2004-05-28 2008-01-11 Toshiba Kk Steam condenser
JP2009097788A (ja) * 2007-10-16 2009-05-07 Toshiba Corp 複圧式復水器及び復水再熱方法
US9857109B2 (en) * 2008-01-02 2018-01-02 Johnson Controls Technology Company Heat exchanger
US8037713B2 (en) 2008-02-20 2011-10-18 Trane International, Inc. Centrifugal compressor assembly and method
US20140034275A1 (en) * 2011-04-21 2014-02-06 Carrier Corporation Condenser/Accumulator and Systems and Operation Methods
US10571168B2 (en) * 2012-09-03 2020-02-25 Trane International Inc. Methods and systems to manage refrigerant in a heat exchanger
WO2014179576A2 (fr) * 2013-05-01 2014-11-06 United Technologies Corporation Evaporateur à flux tombant pour fluides frigorigènes mélangés
JP6295051B2 (ja) 2013-09-26 2018-03-14 荏原冷熱システム株式会社 圧縮式冷凍機用凝縮器

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1641975A (en) * 1926-04-08 1927-09-13 Griscom Russell Co Heat exchanger with self-draining tube surface
EP0962734A2 (fr) * 1998-06-02 1999-12-08 Electric Boat Corporation Echangeur de chaleur

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JP2020506359A (ja) 2020-02-27
ES2945958T3 (es) 2023-07-11
WO2018144215A1 (fr) 2018-08-09
JP6894520B2 (ja) 2021-06-30
CN110249196A (zh) 2019-09-17
EP3577404A1 (fr) 2019-12-11
US20180224172A1 (en) 2018-08-09
US10612823B2 (en) 2020-04-07

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